Clutch



17, 1944- J. E. IVETORINO El'AL 2,350,373

CLUTCH Filed Nov. 12, 1940 2 Sheets-Sheet l nvcniar By @Mm A itorney Oct. 17, 1944. J. E. VETORINO ETAL 2,350,378

CLUTCH Filed Nov. 12, 1940 2 Sheets-$heet 2 Inventor (7 411 l efar/iro A /V0r7na h- G-Ghdron Q By Wm A t t omey Patented Oct. 17, 1944 UNITED STATES PATENT OFFICE CLUTCH John E. Vetorino and Norman R. Gendron, New

Bedford, Mam, assignors to Continental'Machines-y 00., Inc., New Bedford, Man, a corporation-of Massachusetts Application November 12,1040, Serial No. 385,368

19 Claims. (01. 14-2) machine for both washing the laundry and then,

drying it. The machine comprises two wash! containing combination tumbler-and-extractor perforated drums or cylinders, that are permanently mounted at opposite ends of a horizontally disposed carrier shaft. After the cylinders have been loaded with clothes to be laundered. a motor automatically rotates them in a washing fluid about the axis of the horizontally disposed shaft, first in one direction, and then in the opposite direction, alternately. The clothes become thus tumbled in the washing fluid to eflect the washing operation. After the termination of the washing cycle, and with the cylinders still rotating, the washing fluid is drained, after which a,

brake is first released, and a positively driven clutch is then set into action by forcing a plurality of clutch shoes into engagement with a clutch flange that is continuously rotated from the same motor. This results in revolving the cylinders about a vertically disposed axis to extract by centrifugal action the washing fluids still remaining in the laundry after the draining.

The brake is released and the clutch shoes are pressed into engagement with the clutch flange to commence the extracting cycle, at anyspeed of operation of the machine, and at any desired time. In this way, it is possible to transfer, at will, gradually, but positively, from a pure rotation of the cylinders about their horizontally disposed axis to a pure revolution of the cylinders about the vertical axis. During a brief time period, when neither the brake nor the clutch is effective, a combined rotation of the cylinders about their horizontal axis and revolution about the vertical axis takes place. The revolution about the vertical axis is at first slow, but later at gradually increasing speed. The rotation of the cylinders about their horizontal axis gradually decreases. as their revolution about the vertical axis increases. The clutch finally becomes fully effective, and the machine attains its full speed of revolution about the vertical axis, with very little shock and jar. The clutch thereafter remains fully effective to revolvesthe cylinders about the vertical axis to complete the extracting cycle, but without any further rotation of the cylinders about their horizontal axis.

7 sired time, and at any speed of operation of the As the clutch disclosed in the said application, however, is of more general utility than for use in washing machines, an object of the present invention is to provide a new and improved clutch.

Another object is to provide a simply constructed clutch that may be readily and economically installed, and that is adapted for engagement and disengagement at will, at any demachine.

Other and further objects will be explained hereinafter, and will be particularly pointed out in the appended claims.

To the accomplishment of the above objects, a. preferred embodiment of our invention is illustrated in the accompanying drawings, set forth in detail in the succeeding description and defined in the claims appended hereto.

In said drawings:

Figure 1 is a fragmentary view partly in side elevation and partly in vertical section illustrating the preferred embodiment of our invention pplied,

Figure 2 is a view in horizontal section taken on the line 2-2 of Figure 1 and drawn to an enlarged scale,'and

Figure 3 is a view in top plan of the supporting annulus for the brake disengaging member.

The novel clutch of the present invention is illustrated as embodied in a washing machine comprising a cylindrical casing I, closed by a cover 2. Surmounting the cover 2 is a circular cap-like clutch housing 3 concentric to the axis of said casing. Within the top of the housing 3 is a driven pulley 4 horizontally disposed con- ,centricaliy in said housing and having a depending circular clutch flange 5. Within the pulley 4 is a bevel gear 6 having the huh 1 thereof keyed, as at 8, in the hub of said pulley for rotation thereby. The pulley 4 and gear 8 are rotatable axially of the housing 3 on an arbor 9 fixed in the top of the housing. The pulley 4 is driven from a motor, not shown, through the medium of a belt ll of the multiple band type, said pulley being grooved for the specified type of belt. The belt ill extends through suitable apertures, not

. shown, in the housing 3. Within the casing I, in

the vertical axis thereof, is a hollow gear casing I I having a bottom trunnion l2 iournalied in the bottom of the casing and an upper end extending through and Join-nailed inthe cover 2 whereby said gear casing Ii is rotatable about said vertical axis of the casing I. The gear casing ll functions as a carrier for a transverse, short shaft l3 Journalled therein to extend therethrough and having fixed thereon upon opposite sides of the casing 13. pair of combined tumbler and extracting cylinders representedby dotted lines at I4.

The cylinders I4 may be rotated about the axis of their horizontally disposed shaft l3, to tumble their contents, thereby to effect a washing, cleaning or other operation. They may also be revolved as a unit about the vertical axis of the casing I, in unison with the gear casing H upon which they are mounted, to extract liquid from the tumbled contents by centrifugal action. This vertical axis, though between the cylinders I4, is disposed externally of each cylinder individually, near the inner end wall thereof.

The drive for effecting either or both of these actions is obtained from the pulley 4.

Drive is transmitted from the gear 6 to rotate the cylinders 14 about the horizontal axis of the shaft I 3 by means of a bevel gear I5 meshing with the gear 6 and fast on the hub l6 of a sprocket wheel 11. The sprocket wheel I! is ro tatably mounted on a transverse shaft l8 extending through and fixed in the upper end of a tubular bearing sleeve l9 upstanding in the axis of the housing 3 and casing I and supported as presently described. A sprocket chain 20 operatively connects the sprocket wheel I1 to a sprocket wheel 2| fast on the shaft l3 within the gear housing H. For further details of the described washing machine reference may be had to the said application.

The shaft l3, upon which the cylinders l4 are mounted, is thus rotated from the pulley 4 that carries the driven clutch member 5, at a time when the clutch is inefiective, by means of a planetary gear drive comprising the gears 6 and [5, the sprocket wheel ll driven thereby, the sprocket chain 26 and the sprocket wheel 2|. The drive is at this time, not from the driven clutch member 5, but rather from the bevel gear 6, both of which are rotated from the continuously rotated pulley 4 by the belt [0.

According to our invention, drive is transmitted from the pulley 4 to the gear casing II to revolve the same and the cylinders M in unison about the Vertical axis of the casing I and by means of clutch mechanism now to be described.

Fixed in any suitable manner in the upper end of the gear casing ll, within the lower part of the clutch housing 3, and concentric thereto is a disk-like brake plate 22 having an annular concentric bushing 23 upstanding therefrom. The plate 22 carries the before-mentioned bearing sleeve I9 which is suitably secured thereon to extend upwardly therefrom through the bushing 23.

A pair of clutch shoes 24 of segmental form are slidably mounted upon opposite ends of the shaft l8, respectively, intermediate the upper end of the bearing sleeve l9 and the inner face of the flange 5 for movement outwardly and inwardly on said shaft into and from clutching engagement with the inner face of the flange. The clutch shoes 24 are thus fixed to the cylinders l4 to communicate their revolution thereto. Apair of coil springs 25 sleeved onto said shaft l8 between the shoes 24 and the sleeve [9, respectively, urge the shoes outwardly into clutching engagement with the inner face of the rotatable clutch flange 5.- During such clutching engagement, the clutch shoes 24 rotate with the rotatable clutch flange 5. The clutch flange 5 thus constitutes the continuously driven rotatable clutch member and the. clutch shoes 24 the cooperating clutch member of the clutch. The clutch is effective to revolve the cylinders l4 as a unit about the vertical axis when the clutch shoes 24 engage the, clutch flange 5.

In the normal position of the clutch shoes 24, in which the clutch is normally ineffective, the clutch shoes 24 are released from clutching engagement with the clutch flange 5. The clutch shoes 24 may be released from clutching engagement with the clutch flange 5 by sliding them inwardly, as hereinafter described.

Intermediate the clutch shoes 24 and the plate 22 is an annular clutch disengaging member 21 fitting around the upper end of the bushing 23 and rotatable concentrically about the same, said member being also vertically movable on the bushing for a purpose presently seen. A hand lever 28 extends radially outwardly from said member 21 through a slot 21 in the clutch housing 3 and provides for manually rotating said member in opposite directions through a small angular extent. The member 21 is provided with an internally beveled, upstanding, edge flange 29 surrounding the same for ooaction under upward 'movement of the member with camming devices on the clutch shoes 24 to cam said shoes inwardly into disengaging position. Said devices comprise studs 30 extending outwardly from the hubs 3| on the shoes 24 and having anti-friction ball members 32- in the outer ends thereof bearing against the beveled face of the flange 29.

. Below the clutch disengaging member 21 is a supporting annulus 33 therefor fitting around the bushing 23 concentrically of the member 21 and vertically movable on said bushing. Pins 34 of resilient metal extending radially outwardly from said annulus 33 and threaded into tapered plug 35, endwise slidable radially in the housing 3, yieldingly support the annulus for vertical movement from a normal position. Coacting cam lugs 36 and cam notches 31 are provided on the bottom of the clutch disengaging member 21 and in the top of said annulus 33, respectively, the arrangement being such, that under rotation of said member in one direction, said cam lugs 36 and notches 31 will tend to cam the member upwardly and the annulus 33 downwardly.

Intermediate the annulus 33 and the plat 22 is an annular brake disk 38 surrounding the bushing 23 concentrically and fixed to said plate 22 by bolts 39, the disk having on its upper face a suitable brake lining 40 designed to be engaged by the bottom face of the annulus 33 under downward movement of the latter,

When the hand lever 28 is manually actuated clockwise, from the full-line toward the normal dotted-line position of Fig. 2, the brake-disengaging member 21 is likewise actuated clockwise to a corresponding angular extent. By reason of the engagement between the coacting cam lugs 36 and cam notches 31, the brake-disengaging member 21 is at the same time, however, yieldingly carried upward, as viewed in Fig. l, to a small extent, on the cam notches 31,

The brake-disengaging member is thus operable in two directions: .angularly, and by a vertical movement of translation The movement of translation, moreover, automatically accompanies the angular movement, by reason of the ooaction of the cam lugs 36 and the cam notches shoes 24 inward, in opposition to the action of the springs 2|. This will eflect disengagement of the clutch shoes 2| from the clutch flange I of thepulleyl. Thecamnotchesfl maybethus caused to cooperate with the cam lugs 20 during the rotation of the rotatable clutch member I, to cause the cam 22 upon its upper side to disenme the clutch shoes 24 from the clutch flange I, to hold the clutch shoes 24 against further revolution. The brake-disengaging member 21 thus constitutes a clutch-disengaging member, as well.

After the clutch shoes 24 have traveled their maximum distance inward, and the brake-disengagingmemberflhasbeenraisedtothehighest point possible, further pressure on the lever 22 in the same direction, toward the dotted-line position of Fig. 2, will result in forcing the annulus 22 downward to a small extent, in opposition to the force resiliently exerted at this time by the pins 34. When the annulus 22 is thus cammed downward to its lower position, following upon the upward movement of the brake-disengaging member 21, its lower face is forced into braking engagement with the brake lining lll.

The washing or degree-sing Operation is performed during the rotation of the cylinders ll. After this operation has been completed, and while the cylinders l4 are still rotating, the solvent is drained-off. The time has now arrived to actuate the handle 22 in the opposite direction, from the dotted-line position toward the full-line position of Fig. 2, in order to effect extraction, by centrifugal action, of the solvent still remaining in the goods after the draining of the solvent.

Under such operation of said member 21 the annulus 23 rises, under reaction of the pins 24 and disengages from the brake disk 22 to release the gear casing I I for rotation.

When the hand-lever 28 is thus manipulated from the dotted-line toward the full-line position of Fig. 2, the brake-disengaging member 21 will be actuated counter-clockwise. The cam lugs 32 will ride down on the cam notches 31, which will permit the brake-disengaging member 21 to become lowered at the same time that it is actuated counter-clockwise, being cammed down by outward thrust of the balls 32 against the bevelled face of the flange 29 under the urge of the springs 25 against the clutch shoes 24. As the clutch-disengaging member 21 falls, the springs 25 will thrust the ball members 32 outward against the beveled flange 29, to actuate the clutch shoes 2| into clutching engagement with the flange of the driving pulley 4. At the same time, the annulus 23 will be actuated to its upper position, in response to the resilient action of the metal pins 24, thereby to disengage the brake lining 40 on the brake disc 38. In the engaged position of the clutch parts, the drive is transmitted from pulley 4 to shoes 24, to shaft IO, and through the shaft 18 to the bearing sleeve 22, which,-being fixed to the plate 22 and the latter fixed to the gear housing H, imparts rotation to said housing I l.

Three diflerent operations will be described, depending upon whether the lever 28 occupies the normal dotted-line, ineffective position, or the full-line eflective position of Fig. 2, or a position in between (not shown). The pulley l and the bevel gear 6 will be assumed to be continuously driven from the belt H in ,all three positions of the lever 28.

When the lever 28 occupies the normal dottediine position 01 Fig. 2, the brake-disengaging member 21 occupies its upper position, in which the clutch shoes 24 are disengaged from the flangev I, so that the clutch is ineflective, and the annulus "its lower position, in which it engages the'brake disc 88. The cylinders it are therefore free to rotate about the axis of the horizontally disposed cylinder-carrying shaft l2; and the brake disc as, in this normal position, prevents their revolution, with their carrier casing ll, about the vertically disposed axis of the carrier casing I I. The normal dotted-line position may therefore be termed the cylinder-rotation position, because the drive of the cylinders from the driven clutch member 5, when the lever 22 cccupies this position, is constituted of a pure rotation about the horizontal axis. The full-line position may similarly be termed the cylinderrevolution position, because the drive of the cylinders from the clutch members 5 and 24, when the lever 28 occupies this position, is a revolution of the cylinders about the vertical axis. In the intermediate position (not shown) of this lever 22, the connection of the driven cylinders H to the driven clutch member 5 is such that acombined movement of rotation about the horizontal axis and revolution about the vertical axis is imparted to the cylinders.

Referring first to the operation that takes place wh n th lever 18 pies the dotted-line, 0r rotation, position of Fig. 2, in this normal position, the brake is effective to prevent revolution of the carrier II and the cylinders 14 carried thereby, and the clutch is ineffective. The rotation of the bevel gear 8 is converted into rotation of the bevel gear II that meshes therewith,

and of the horizontally disposed shaft l8 upon which the bevel gear I! is mounted. The resulting rotation of the sprocket wheel I! is communicated to the sprocket chain 20, and this effects rotation of the sprocket driving wheel 2|. The rotation of the sprocket wheel 2| is communicated to the shaft l3 and to the cylinders it carried thereby. In this dotted-line position of the lever 22, therefore, the drive from the pulley l, the bevel gears 6 and It, the sprocket wheels I] and 2|, and the sprocket chain 20 is transmitted to the shaft H to rotate the cylinders ll, with the horizontally disposed shaft l3 to which they are secured, in unison about the axis of this shaft I3, but they are at this time pre vented from revolving about the vertical axis. The cylinders H become thus rotated about their horizontal axis at a time when they are braked against revolution about the vertical axis.

This rotation of the cylinders results in tumbling or agitating the laundry or the like in the said solvent fluids, which may effect the washing of laundry, or other desired treatment.

For the purpose of extracting, though other uses are also contemplated, the invention provides also for transmitting the drive from the clutch flange 5 of the pulley l to the gear casing H, thus to revolvethe casing H and the cylinders It in unison about the vertical axis of the casing i.

When the lever 28 occupies its full-line, or revolution, position of Fig. 2, the brake-disengaging member 21 occupies its lower position, to permit the clutch shoes 24 to engage the clutch flange I; and the annulus 33 occupies its upper position, out of engagement with the revolution- I preventing brake disc 38. The brake disc 38 is therefore released, or rendered ineflective, rendering the gear casing H, with the cylinders I4 carried thereby, free to revolve about its vertical comes revolved about the vertical axis, also. In

this position of the lever 28, therefore. the drive is communicated directly from the flange 5 of the pulley 4, through the clutch shoes 24, solely to the gear casing I I and the parts carried thereby, the bevel gears 6 and I5 acting at this time as though they were rigidly locked together to revolve as a unit about the vertical axis, without relative rotation, and without the bevel gear l5 turning on its own axis. Under these conditions, the casing H, together with the cylinders l4, and the other parts carried thereby, including the sprocket wheel H, the cross-shaft I8, the clutch shoes 24 mounted thereon, and the brake plate 22, will revolve as a unit about the vertical axis, in the same direction throughout, without any rotation of the cylinders l4 about their horizontal axis. a

It is now in Ol'dx: to consider what takes place at an intermediate time, after the lever 28 has been actuated out of its dotted-line position, but before the pure revolution before described takes place. For purposes of clarity of explanation, let it first be assumed that the handle 28 is maintained in an intermediate position (not shown) between the full-line and the dotted-line positions of Fig, 2. In this intermediate position, both the clutch and the brake are ineffective; the clutch shoes 24 do not effectively engage the flange 5, and the annulus 33 does not effectively engage the brake disc 38.

Because the clutch is ineffective, the cylinders M will still be rotated about their horizontal axis from the driven clutch member 4 through the bevel gears 6 and IS, the sprocket gear II, the sprocket chain 28 and the sprocket gear 2|. The inertia of the cylinders I 4 with their loads, however, will tend to oppose the rotation of the cylinders l4 about their horizontally disposed axis. There will therefore be a tendency for the gears 6 and I5 to become locked against relative rotation to some extent. This tendency will not now be opposed, however, because the brake is likewise ineffective. There will consequently result a part rotation of the bevel gear l5 about its own axis from the bevel gear -ii, and a part revolution of these bevel gears 6 and I5 as a unit about the vertical axis. As a consequence, there will take place a combined rotation of the cylinders l4 about their horizontal axis and revolution of the cylinders about the vertical axis, this combined rotation and revolution being both effected from the rotation of the bevel gear 6 alone, under drive from the belt l0, and without the loads on the two cylinders be unequal, therefore, they will so re-arrange themselves as to cause the cylinders and their loads to become very evenly balanced. This balance prevents uneven cen-- trifugal stress'from straining or damaging the machine during the extracting cycle.

At first, the speed of rotation of the cylinders about their horizontal axis will be large, and their speed of revolution about the vertical axis small. The speed of revolution, however,' will gradually increase and that of rotation will gradually decrease. When the speed of revolution becomes sufllciently great, the lever 28 may be actuated from the intermediately disposed position (not shown) to the full-line position of Fig. 2. The clutch shoes 24 will thus be caused to grip against the clutch flange 5 at a time when they are already revolving about the vertical axis at a speedmore or less approaching the speed of the clutch flange 5 itself. The clutch shoes 24 will therefore eflect their clutching engagement against the clutch flange 5 with a of shock and Jar. From that time on, moreover, the clutch shoes 24 will assure pure revolution of the cylinders l4 and their loads about the vertical axis, and without any further rotation of the cylinders about their horizontal axis. The rotation of the cylinders l4 around the horizontal ax s is thereafter completely stopped, and the sole motion is a revolution about the vertical axis. This condition will obtain as long as the clutch remains effective.

The above description has been upon the sup-' position that the lever 28 is maintained in its intermediately disposed position (not shown), following upon the completion of the washing or degreasing cycle, until the machine picks up speed. In actual practice, it is not necessary that the lever 28 be held in the intermediately disposed position. It may be actuated directly from the dotted-line to the full-line position of Fig. 2, and the same effect will take place.

This is because, upon the actuation of the lever 28 from the dotted-line toward the fullline position of Fig. 2, the brake 38 releases before the clutch shoes 24 become effective. Even though theclutch lever 28 be actuated directly from the dotted-line position to the full-line position of Fig. 2, therefore, there will be a brief interval of time following upon the release of the brake, and before the clutch shoes become efiective, during which the brake and the clutch are both inefiective, and during which the combined rotation and revolution of the cylinders I4 takes place under drive from the motor, in the same manner as before described. Because of the existence of this brief period of time subsequent to the pure rotation of the cylinders and prior to their pure revolution, there is the same tendency as before described to reduce shock and jar.

Such shock and jar as might still be introduced by too early engagement of the clutch shoes 24 with the clutch flange 5, moreover, may be further minimized by suitable adjustment of the tension of the springs 25, and of the degree of inward and outward movement of the clutch shoes 24, to ensure that the clutch shoes 24 shall not grip too firmly to start out with against the clutch flange 5, but shall grip rather with a slip action until after a predetermined time delay. Further rotation of the cylinders l4 about their horizontal axis may thus be prevented at any desired time, during the combined rotation and revolution of the cylinders, after the brake has been rendered ineffective.

Owing to the before-described inertia of the cylinders I4 and the loads contained therein,

the clutch shoes 24 will not immediately clutch positively against the flange 5 as soon as they engage this flange, but they will slip to some extent. Owing to this slip, the cylinders II will continue to rotate to some extent about the axis of the horizontal shaft I! at the same time that they revolve about the vertical axis, in the same way as already explained. The rate of slippage gradually decreases until, finally, the clutch shoes 24, under the action of the springs 25, become enabled to grip the clutch flange 5 positively with sumcient force. Thereafter, the springs 25 will maintain the clutch shoes 24 effective. From that time on, therefore, there will be no further rotation of the cylinders 14 about the axis of the horizontal shaft it, but the entire motion of the cylinders M will be a revolution about the vertical axis.

When the cylinders II have been revolved sumciently about the vertical axis to complete the extracting cycle, the hand lever 28 may finally be returned to its normal dotted-line position once more. This restores the brake-disengaging member 21 to its upper position, and the annulus 33 to its lower position. The clutch shoes 24, therefore, become again disengaged from the clutch flange 5, and the annulus 31 becomes again actuated into engagement with the brake lining 40 on the brake disc 38. The revolution of the gear casing H, with the cylinders l4 and the other parts carried thereby, will thereupon become first retarded, and then ultimately stopped. Meantime, owing to continued rotation of the pulley l by the belt 10, the drive becomes again automatically transmitted from the bevel gear i to the bevel gear l5 and thence, by the sprocket-and-chain mechanism, to the shaft It, thus restoring the previously described rotation of the cylinders ll about the horizontally disposed axis of the shaft II.

For a time, therefore, there will again be a combined rotation of the cylinders about their horizontal axis and revolution about the vertical axis. This results in tumbling the clothes still further. This is advantageous, because the goods in the cylinders become opened out thereby.

This final combined rotating-and-revolving movement of the cylinders, subsequent to the extracting operation, may be effected at a time when the power from the belts I is shut oil, and wholly by the inertia of the moving cylinders and their loads; the motor may be disconnected from the line. Though no power is at this time obtained from the motor, the machine will continue its combined rotation and revolution of the cylinders by its own inertia if the motor switch is opened while the cylinders are still revolving. During the continued revolution of the machine about the vertical axis by its inertia, there is introduced also a rotation of the cylinders about their horizontal axis, caused by relative movement of the gears 6 and i5, as before described. The gears 6 and I lock to some extent, to permit revolution of the cylinders, but/they rotate also with respect to'each other to some extent, to permit rotation of the cylinders.

A machine is thus provided by the present invention that positively, and without fail, will perform the functions demanded of it. When the hand lever 28 occupies its extreme normal dotted-line position, the motion of the cylinders ll will be a pure rotation about their horizontal axis, revolution about the vertical axis being, at this time, prevented by the annulus 33 engaging the brake lining I. upon the brake disc 38.

Upon the actuation of the lever 28 to its extreme full-line position, a suitable time interval will ensue, the length of which may be adjusted, during which there will be combined rotation of the cylinders about the horizontal axis and revolution of the cylinders as a unit about the vertical axis. The speed of revolution about the vertical axis gradually increases, and the rotation about the horizontal axis gradually decreases, until the speed of rotation about the horizontal axis stops altogether, at a time determined by the adjustment. The sole motion thereafter is a pure revolution only of the cylinders about their vertical axis as a unit, without horizontal rotation. By actuating the lever 28 to an intermedi-' ate position, where such may be desired, it is possible also to obtain combined rotation of the cylinders about the horizontal axis and revolution about the vertical axis, until the machine runs down by its inertia.

Modifications will occur to persons skilled in the art, and all such are considered to fall within the spirit and scope of the invention, as defined in the appended claims.

What is claimed is:

1. A machine of the class described having, in combination, a rotatable clutch member, a cooperating clutch member, means for maintaining the cooperating clutch member in engagement with the rotatable clutch member during the rotation of the rotatable clutch member to cause the cooperating clutch member to rotate in response to the rotation of the rotatable clutch member, a disengaging member having two earns, a cam for engaging one of the two cams during the rotation of the rotatable clutch member to cause the other of the two cams to disengage the cooperating clutch member from the rotatable clutch member to hold the cooperating clutch member against rotation, a rotatable member, and means operable during the rotation of the rotatable clutch member and while the cooperating clutch member is held against rotation for rotating the rotatable member.

2. A machine of the class described having, in combination, a rotatable clutch member, a cooperating clutch member, means whereby the cooperating clutch member may be caused to engage the rotatable clutch member during the rotation of the rotatable clutch member to cause the cooperating clutch member to rotate in response to the rotation of the rotatable clutch member, a cam, a third member having a cooperating cam for engaging the first-named cam, means for actuating the third member to cause the cooperating cam to engage the first-named cam during the rotation of the rotatable clutch member to disengage the cooperating clutch member from the rotatableclutch member and to hold the cooperating clutch member against rotation, a rotatable member, and means controlled by the third member when actuated by the actuating means and operable during the rotation of the rotatable clutch member and while the cooperating clutch memberv is held against rotation for rotating the rotatable member.

3. A machine of the class described having, in combination, a shaft, means for rotating the shaft about its axis, means for revolving the shaft about a second axis at right angles to the shaft axis, the revolving means comprising a rotatable clutch member, a cooperating clutch member, and

. means for maintaining the cooperating clutch clutch member to cause the cooperating clutch member to rotate in response to the rotation of the rotatable clutch member, a disengaging member operable angularly and by a movement or translation, coacting camming devices on the disengaging member and the cooperating clutch member, respectively, for disengaging the cooperating clutch member from the rotatable clutch member when the disengaging member is actuated angularly, means for actuating the dis-' engaging member anguiarly, and means for actuating the disengaging member by a movement of translation when it is moved angularly.

4. A machine of the class described having, in combination, a shaft, means for rotating the shaft about its axis, means for revolving the shaft about a second axis at right angles to the shaft axis, the revolving means comprising a rotatable clutch member, a cooperating clutch member, and means for maintaining the cooperating clutch member in engagement with the ro tatable clutch member during the rotation of the rotatable clutch member to cause the cooperating clutch member to rotate in response to the rotation of the rotatable clutch member, a disengaging member, means for actuating the disengaging member in two directions, coacting camming devices on the disengaging member and the cooperating clutch member, respectively, for disengaging the cooperating clutch member from the rotatable clutch member when the disengaging member is actuated in one direction, and means for actuating the disengaging member in both directions when actuated in one direction.

5. A machine of the class described having, in combination, a shaft, means for rotating the shaft about its axis, means for revolving the shaft about a second axis at right angles to the shaft axis; the revolving means comprising a rotatable clutch member, a cooperating clutch member, and means for maintaining the cooperating clutch member in engagement with the rotatable clutch member during the rotation of the rotatable clutch member to cause the cooperating clutch member to rotate in response to the rotation of the rotatable clutch member, a disengaging member, means for actuating the disengaging member in two directions, coacting camming devices on the disengaging member and the cooperating clutch member, respectively, for disengaging the cooperating clutch member from the rotatable clutch member when the disengaging member is actuated in one direction, and means for actuating the disengaging member in both directions when actuated in one direction, the last-named means comprising an annulus and coacting camming devices on the annulus and the disengaging member, respectively.

6. A machine of the class described having, in combination, a shaft, means for rotating the shaft about its axis, means for revolving the shaft about a second axis at right angles to the shaft axis, the revolving means comprising a rotatable clutch member, a cooperating clutch member, and means for maintaining the cooperating clutch member in engagement with the rotatable clutch member during the rotation of the rotatable clutch member to cause the cooperating clutch member to rotate in response to the rotation of the rotatable clutch member, a disengaging member, means for actuating the disengaging member in two directions, and coacting camming devices on the disengaging member and the cooperating clutch member, respectively, for disengaging the cooperating clutch member from the rotatable clutch member when the disengaging member is actuated in one direction, the camming devices comprising an an-. nular flange on the disengaging member having a beveled internal face and spring-pressed members on the cooperating clutch member bearing against said face.

7. A machine of the class described having, in combination, a shaft, means for rotating the shaft about its axis, means for revolving the shaft about a second axis at right angles to the shaft axis, the revolving means comprising a rotatable clutch member, a cooperating clutch member, and means for maintaining the cooperating clutch member in engagement with the rotatable clutch member during the rotation of the rotatable clutch member to cause the cooperating clutch member to rotate in response to the rotation of the rotatable clutch member, a disengaging member, means for actuating the disengaging member in two directions, coacting camming devices on the disengaging member and the cooperating clutch member, respectively, for disengaging the cooperating clutch member from the rotatable clutch member when the disengaging member is actuated in one direction, and a brake disk for frictionally retarding the revolution of the shaft upon the disengagement of the cooperating clutch member from the rotatable clutch member.

8. A.machine of the-character described having, in combination, a normally ineffective clutch comprising a driven clutch member and a cooperating clutch member; means for continuously 35 driving the driven clutch member; a driven member rotatable about one axis and revoluble about another axis; means connecting the driven member to the driven clutch member to rotate the driven member about the said one axis and to 40 revolve it about the said other axis; means effective normally, when the clutch is ineffective, to prevent the revolution of the driven member about the said other axis, whereby, normally, when the clutch is ineffective, the driven mem- 45 ber is rotated about the said one axis from the driven clutch member but without being revolved about the said other axis; means for rendering the preventing means ineffective, whereupon a combined rotation about the said one axis and 50 revolution about the said other axis becomes imparted to the driven member from the driven clutch member; normally ineffective mea'ns operable when effective to render the clutch effective and thereafter to maintain the clutch effec- 65 tive; means connecting the driven member to the cooperating clutch member to revolve the driven member about the said other axis from the cooperating clutch member when the clutch is effective; and means operable during the said combined rotation and revolution of the driven member to prevent its further rotation at any desired time after the revolution-preventing means has been rendered ineffective, whereby, thereafter, during the efl'ectiveness of the means for rendering and maintaining the clutch effective, the driven member is revolved about the said other axis but without being rotated about the said one axis.

9. A machine of the character described having, in combination, a normally ineffective clutch comprising a driven clutch member and a cooperating clutch member; means for continuously driving the driven clutch member; a driven mem, ber rotatable about one axis and revoluble about 76 another axis; means connecting the driven member to the driven clutch member to rotate the driven member about the said one axis and to revolve it about the said other axis; means effective normally, when the clutch is ineffective, to prevent the revolution of the driven member about the said other axis, whereby, normally, when the clutch is ineffective, the driven member is rotated about the said one axis from the driven clutch member but without being revolved about the said other axis; means for rendering the preventingmeans ineffective, whereupon a combined rotation about the said one axis and revolution about the said other axis becomes imparted to the driven member from the driven clutch member; normally ineffective means operable when effective to render the clutch effective and thereafter to maintain the clutch effective; means connecting the driven member to the cooperating clutch member to revolve the driven member about the said other axis from the cooperating clutch member when the clutch is effective; means operable during the saidcombined rotation and revolution of the driven member to prevent its further rotation at any desired time after the revolution-preventing means has been rendered ineffective, whereby, thereafter, during the effectiveness of the means for rendering and maintaining the clutch effective, the driven member is revolved about the said other axis but without being rotated about the said one axis; and means for controlling the time at which the said further rotation of the driven member is prevented.

10. A machine of the character described having, in combination, a clutch comprising a rotatable clutch member and a cooperating clutch member; means for continuously rotating the rotatable clutch member; normally ineffective means tending to actuate the cooperating clutch member into clutching engagement with the rotatable clutch member; means for preventing the rotation of the cooperating clutch member when the tending means is ineffective; a driven member rotatable about one axis and revoluble about another axis; means connecting the driven member to the rotatable clutch member to rotate the driven member about the said one axis and to revolve it about the said other axis; means for preventing the revolution of the driven member about the said other axis, whereby, when the cooperating clutch member is out of clutching engagement with the rotatable clutch member, the driven member is rotated about the said one axis from the rotatable clutch member but without being revolved about the said other axis; means for rendering the preventing means ineffective, whereupon a combined rotation about the said one axis and revolution about the said other axis becomes imparted to the driven member from the rotatable clutch member; normally ineffective means operable when effective to render the tending means effective to actuate the cooperating clutch member into clutching engagement with the rotatable clutch member and thereafter to maintain the cooperating clutch member inengagement with the rotatable clutch member; means connecting the driven member to the cooperating clutch member to revolve the driven member about the said other axis from the cooperating clutch member when the cooperating clutch member is in engagement with the rotatable clutch member; and means operable during the said combined rotation and revolution of th driven member to prevent its further rotation at any desired time after the revolution-preventing means has been rendered ineffective, whereby, thereafter, during the effectiveness of the means for rendering and maintaining the clutch effective, the driven member is revolved about the said other axis but without being rotated about the said one axis.

11. A machine of the character described having, in combination, a normally ineffective clutch comprising a clutch member rotatable about a first axis and a cooperating clutch member; means for continuously rotating the rotatable clutch member about the first axis; a bevel gear rotatable with the rotatable clutch member about the first axis; abevel gear meshing with the first-named bevel gear and rotatable about a second axis; the second-named bevel gear being revolvable about the first axis in response to the rotation of the first-named bevel gear when the second-named bevel gear is prevented from rotating about the second axis; the cooperating clutch member being non-rotatable with respect to the second-named bevel gear but being rotatable with the second-named bevel gear about the first axis; a driven member rotatable about a third axis and revoluble about the first axis; means connecting the driven member to the second-named bevel gear to rotate the driven member about the third axis and to revolve it about the first axis; means effective normally, when the clutch is ineffective, to hold the secondnamed bevel gear and the cooperating clutch member against rotation about the first axis during the rotation of the driven member, whereby, normally, when the clutch is ineffective, the driven member is rotated about the third axis from the rotatable clutch member but without being revolved about the first axis; means for rendering the holding means ineffective, whereupon the second-named bevel gear becomes rotatable about the second axis in response to the rotation of the first-named bevel gear about the first axis to effect a combined rotation of the driven member about the third axis and revolution thereof about the first axis from the rotatable clutch member; normally ineffective means operable when effective to render the clutch effective and thereafter to maintain the clutch effective; means connecting the driven member to the cooperating clutch member to revolve the driven member about the first axis from the cooperating clutch member when the clutch is effective; and means operable during the said combined rotation and revolution of the driven member to revolve the driven member with the second-named bevel gear about the first axis, thereby to prevent further rotation of the driven member at any desired time after the holding means has been. rendered ineffective, whereby, thereafter, during the effectiveness of the means for rendering and maintaining the clutch effective, the driven member is revolved about the first axis but without being rotated about the third axis.

12. A machine of the character described having, in combination, a normally ineffective clutch comprising a clutch member rotatable about a first axis and a cooperatin clutch member; the rotatable clutch member having a clutch flange and the cooperating clutch member having a clutch shoe disposed in the flange that is adapted to be actuated into engagement with the flange to render the clutch effective; means for continuously rotating the rotatable clutch member about the first axis; a bevel gear disposed in the flange to rotate with the rotatable clutch member about the first axis; a bevel gear disposed in the flange to i'nesh with the first-named bevel gear and rotatable about a second axis; the second-named bevel gear being revoluble about the first axis in response to the rotation of the firstnamed bevel gear when the second-named bevel gear is prevented from rotating about the second axis; the cooperating clutch member being non-rotatable with respect to the second-named bevel gear but being rotatable with the secondnamed bevel gear about the first axis; a driven member rotatable about a third axis and revoluble about the first axis; means connecting the driven member to the second-named bevel gear to rotate the driven member about the third axis and revolve it about the first axis; a brake effective normally, when the clutch is ineffective, to hold the second-named bevel gear and the cooperating clutch member against rotation about the first axis during the rotation of the driven member about the third axis, whereby, normally, when the clutch is ineffective, the driven member is rotated about the third axis from the rotatable clutch member but without being revolved about the first axis; means operable during the rotation of the driven member about the third axis for releasing the brake, whereupon the second-named bevel gear becomes rotatable about the second axis in response to the rotation of the first-named bevel gear about the first axis to effect a combined rotation of the driven member about the third axis and revolution thereof about the first axis from the rotatable clutch member; normally ineffective means operable when effective to render the clutch effective and thereafter to maintain the clutch effective; means connecting the driven member to thecooperating clutch member to revolve'the driven-member about the first axis from the cooperating clutch member when the clutch is effective; and means operable during the said combined rotation and revolution of the driven member to revolve the driven member as a unit with the second-named bevel about the first axis, thereby to prevent further rotation of the driven member at any desired time after the brake has been released, whereby, thereafter, during the effectiveness of the means for rendering and maintaining the clutch effective, the driven member is revolved about the first axis but without being rotated about the third axis.

13. A machine of the character described having, in combination, a normally ineffective clutch comprising a clutch member rotatable about a first axis and a cooperating clutch member; the rotatable clutch member having a clutch flange and the cooperating clutch member having a clutch shoe disposed in the flange that is adapted to be actuated into engagement with the flange to render the clutch effective; means for continuously rotating the rotatable clutch member about the first axis; a bevel gear disposed in the flange to rotate with the rotatable clutch member about the first axis; a bevel gear disposed in the flange to mesh with the first-named bevel gear and rotatable about a second axis; the second-named bevel gear being revoluble about the first axis in response to the rotation of the firstnamed bevel gear when the second-named bevel gear is prevented from rotating about the second axis; the cooperating clutch member being nonrotatable with respect to the second-named bevel gear but being rotatable with the second-named bevel gear about the first axis; a driven member having an axis at right angles to the first axis; a

shaft coaxial with the driven member and upon which the driven member is mounted; a carrier rotatable with the cooperating clutch member; the shaft and the driven member mounted thereon being carried by the carrier so. as to revolve during the rotation of the carrier about the first axis; a sprocket gear rotatable with the secondnamed bevel gear, a sprocket gear connected to the shaft, and a sprocket chain mounted over the sprocket gears, whereby the shaft and the driven member will be rotated about the axis of the driven member and the carrier will be rotated to effect revolution of the shaft and the.

driven member about the first axis; a brake effective normally, when the clutch is ineffective, to hold the second-named bevel gear and the cooperating clutch member, together with the carrier, against rotation about the first axis during the rotation of the shaft, whereby, normally, when the clutch is ineffective, the driven member is rotated about its axis from the rotatable clutch member but without being revolved about the first axis; means operable during the rotation of the driven member about its axis for releasing the brake, whereupon the second-named bevel gear becomes rotatable about the second axis in response to the rotation of the first-named bevel gear about the first axis to effect a combined rotation of the driven member about its axis and revolution thereof about the first axis from the rotatable clutch member; normally inefiective means, operable when effective to render the clutch effective and thereafter to maintain the clutch effective; means connecting the driven member to the cooperating clutch member to revolve the driven member about the first axis from the cooperating clutch member when the clutch is effective; and means operable during the said combined rotation and revolution of the driven member to revolve the driven member and the shaft upon which it is mounted as a unit with the second-named bevel gear about the first axis, thereby to prevent further rotation of the driven member-at any desired time after the brake has been released, whereby, thereafter, during the effectiveness of the means for rendering and maintaining the clutch effective, the driven member is revolved about the first axis but without being rotated about its axis.

14. A machine of the class described having, in combination, a shaft having a horizontal axis and revoluble about a vertical axis, means comprising a driven clutch member rotatable about the vertical axis for rotating the shaft about the horizontal axis, means for revolving the shaft under operation of the clutch member comprising a pair of oppositely disposed clutch shoes and means for yieldingly pressing the shoes into engagement with the clutch member, means for disengaging the shoes from the clutch member comprising an annular member disposed concentrically with the vertical axis below the clutch member for vertical and angular movement, coacting camming devices on the angular member and the shoes, respectively, for disengaging the shoes under upward movement of the annular member, and means for causing upward movement of the annular member in response to angular movement thereof in one direction.

15. A machine of the class described having, in combination, a shaft having a horizontal axis and revoluble about a vertical axis, means comprising a driven clutch member rotatable about the vertical axis for rotating the shaft about the horizontal axis, means for revolving the shaft under operation of the clutch member comprising a pair of oppositely disposed clutch shoes and means for yieldingly pressing the shoes into engagement with the clutch member, means for disengaging the shoes from the clutch member comprising an annular member disposed cncen-' trically with the vertical axis below the clutch member for vertical and angular movement, coacting camming devices on the ,annular member and the shoes, respectively, for disengaging the shoes under upward movement of the annular member, and means for causing upward movement of the annular member in response to angular movement thereof in one direction, the last-named means comprising an annulus mounted below the annular member and coacting camming devices on the annulus and the annular member, respectively.

16. A machine of the class described having, in combination, a shaft having a horizontal axis and revoluble about a vertical axis, means comprising a driven clutch member rotatable about the vertical axis for rotating the shaft about the horizontal axis, means for revolving the shaft under operation of the clutch member comprising a pair of oppositely disposed clutch shoes and spring-pressed members on the shoes for pressing the shoes into engagement with the clutch member, the clutch member having an annular flange provided with a beveled internal face, the. spring-pressed members bearing against the beveled face, and means for disengaging the shoes from the clutch member, the disengaging means comprising an annular member disposed concentrically with the vertical axis below the clutch member for vertical and angular movement, means for disengaging the spring-pressed members from the beveled face under upward movement of the annular member, and means for causing upward movement of the'annular member in response to angular movement thereof in one direction.

17. A machine of the class described having, in combination, a shaft having a horizontal axis and revoluble about a vertical axis, means com-- mtauy with the vertical axis below the clutch 55 member for vertical and angular movement, coacting camming devices on the annular member and the shoes, respectively, for disengaging the shoes under upward movement of the annular member, means for causing upward movement of the annular member in response to angular movement thereof, in one direction, and means for frictionally retarding the revolution of the shaft about the vertical axis.

18. A machine of the class described having, in combination, a shaft having a horizontal axis and revoluble about a vertical axis, means comprising a driven clutch member rotatable about the vertical axis for rotating the shaft about the horizontal axis, means for revolving the shaft under operation of the clutch member comprising a pair of oppositely disposed clutch shoes and means for yieldingly pressing the shoes into engagement with the clutch member, means for disengaging the shoes from the clutch member comprising an annular member disposed concentrically with the vertical axis below the clutch member for vertical and angular movement, coacting camming .devices on the annular member and the shoes, respectively, for disengaging the shoes under upward movement of the annular member, means for causing upward movement of the annular member in response to angular movement thereof in one direction, the last-named means comprising an annulus mounted below the annular member and enacting camming devices on the annulus and the annular member, respeo tively, and means for frictionally retarding revolution of the shaft about the vertical axis comprising a brake disk mounted to revolve with the shaft, the annulus being resiliently mounted for engagement with the disk and operative under the coaction of the camming devices into engagement therewith.

19.A machine of the character described having, in combination, a normally ineffective clutch comprising a driven clutch member and a cooperating clutch member, means for continuously driving the driven clutch member, a driven member; means connecting the driven member to the driven clutch member to rotate the driven mem-* a time interval and then fully effective and for thereafter maintaining the clutch eil'ective, and means connecting the driven member to the cooperating clutch member to revolve the driven member from the cooperating clutch member when the clutch is effective, the connecting means of the driven member to the clutch members preventing rotation of the driven member during its revolution when the clutch is fully eifective but permitting both rotation and revolution of the driven member during the time interval.

JOHN E. VETORINO. NORMAN R. GENDRON. 

